U.S. patent number 10,072,758 [Application Number 14/935,897] was granted by the patent office on 2018-09-11 for stuffing box body with integral diverted lantern ring.
This patent grant is currently assigned to SEAL RYT CORPORATION. The grantee listed for this patent is SEAL RYT CORPORATION. Invention is credited to Andrew J. Getto, Michael F. Huard.
United States Patent |
10,072,758 |
Getto , et al. |
September 11, 2018 |
Stuffing box body with integral diverted lantern ring
Abstract
A bearing with an integral diverted lantern ring for
installation into the seal cavity of a rotary mechanical device to
provide a bearing surface and allow for flush fluid to engage the
shaft closer to the motor end is provided. The bearing eliminates
whip in a rotating shaft and is split to allow easy installation
over an installed shaft. The bearing is substantially cylindrical
with an inner bore closely approximating the outer diameter of the
shaft. The diverted lantern ring includes an outer groove at the
impeller end on the outer surface at a flush port and a groove on
the inner surface at a location closer to the motor end. Flush
fluid channels are provided between the outer groove and inner
groove of the bearing. The purpose is to redirect the external
flush from the impeller end on the OD to the motor end on the ID,
thus repositioning the flush deposit on the sleeve, under the
bearing. This allows the throttling characteristic of the close
clearance bearing surface to increase.
Inventors: |
Getto; Andrew J. (Agawam,
MA), Huard; Michael F. (Easthampton, MA) |
Applicant: |
Name |
City |
State |
Country |
Type |
SEAL RYT CORPORATION |
Westfield |
MA |
US |
|
|
Assignee: |
SEAL RYT CORPORATION
(Westfield, MA)
|
Family
ID: |
57421944 |
Appl.
No.: |
14/935,897 |
Filed: |
November 9, 2015 |
Prior Publication Data
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|
|
|
Document
Identifier |
Publication Date |
|
US 20170130729 A1 |
May 11, 2017 |
|
Current U.S.
Class: |
1/1 |
Current CPC
Class: |
F04D
29/049 (20130101); F16J 15/40 (20130101); F04D
29/10 (20130101); F16C 33/74 (20130101); F04D
1/00 (20130101); F16J 15/183 (20130101); F04D
29/0462 (20130101); F16J 15/182 (20130101); F16J
15/406 (20130101); F04D 29/108 (20130101) |
Current International
Class: |
F16J
15/18 (20060101); F16C 33/74 (20060101); F04D
29/10 (20060101); F16J 15/40 (20060101) |
References Cited
[Referenced By]
U.S. Patent Documents
Foreign Patent Documents
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3028537 |
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Feb 1981 |
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DE |
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191311868 |
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May 1914 |
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GB |
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2056588 |
|
Mar 1981 |
|
GB |
|
Primary Examiner: Foster; Nicholas L
Attorney, Agent or Firm: Wolfson; Michael I. Dippert;
William H.
Claims
What is claimed is:
1. A bearing with an integral diverted lantern ring for use in an
annular seal cavity of a rotary mechanical device having an output
end and a power end with a shaft running through the seal cavity,
comprising: a substantially rigid cylindrical body dimensioned to
fit into the annular seal cavity of the rotary mechanical device; a
sidewall of the bearing having an outer cylindrical surface closely
dimensioned to fit into the seal cavity and having an inner bore
closely dimensioned to fit over the shaft at one end of the seal
cavity to provide a bearing surface for the shaft; the outer
cylindrical surface of the bearing formed with an outer groove with
at least one flush hole, and the inner bore of the bearing formed
with an inner groove with at least one flush hole, the inner groove
at a location spaced apart from and not aligned with the outer
groove along the longitudinal axis of the bearing to form a
displaced integral lantern ring; the at least one flush hole in the
outer groove extending substantially radially into the sidewall to
a predetermined depth and the at least one flush hole in the inner
groove extending substantially radially into the sidewall to a
predetermined depth; and at least one substantially axial flush
passage in the sidewall at the predetermined depths connecting the
at least one flush hole in the outer groove and the at least one
flush hole in the inner groove to form a non-linear path between
the inner and outer grooves within the sidewall for passage of seal
fluid through the bearing to the shaft.
2. The bearing of claim 1, wherein the outer groove is closer to
the output end.
3. The bearing of claim 1, wherein the substantially rigid
cylindrical body is split axially into two halves to facilitate
installation over the shaft.
4. The bearing of claim 1, wherein the substantially rigid
cylindrical body is formed of a non-ferrous metal material.
5. The bearing of claim 1, wherein the substantially rigid
cylindrical body is formed from a molybdenum and carbon filled
thermoplastic material.
6. The bearing of claim 1, wherein the outer groove at the output
end has a width that is narrower than a length of the outer
cylindrical surface at the power end.
7. The bearing of claim 1, wherein the inner groove at the power
end has a width that is narrower than a length of the outer
cylindrical surface at the output end.
8. The bearing of claim 3, wherein corresponding alignment holes
are formed in each of the split halves, and alignment pins are
positioned in the alignment holes.
9. The bearing of claim 1, wherein the outer cylindrical surface
includes an O-ring groove between the outer groove and the output
end, and an O-ring is disposed in the O-ring groove.
10. The bearing of claim 1, further including at least one
compressible packing ring disposed on the power side of the
substantially rigid cylindrical body in the seal cavity.
11. A shaft sealing system for use in an annular seal cavity of a
mechanical device having an output end and a power end with a shaft
running through the seal cavity, comprising: a substantially rigid
cylindrical body having a sidewall dimensioned to fit into the seal
cavity about the shaft; the sidewall of the body having an outer
cylindrical surface closely dimensioned to fit into the seal cavity
and having an inner bore closely dimensioned to fit over the shaft;
the outer cylindrical surface formed with an outer groove with at
least one flush hole, and the inner bore formed with an inner
groove with at least one flush hole, the inner groove at a location
spaced apart from and not aligned with the outer groove along the
longitudinal axis of the cylindrical body to form a displaced
integral lantern ring; the at least one flush hole in the outer
groove extending substantially radially into the sidewall to a
predetermined depth and the at least one flush hole in the inner
groove extending substantially radially into the sidewall to a
predetermined depth; and at least one substantially axial passage
in the sidewall at the predetermined depths connecting the at least
one flush hole in the outer groove and the at least one flush hole
in the inner groove to form a non-linear path between the inner and
outer grooves within the sidewall for passage of seal fluid through
the displaced integral lantern ring and to the shaft.
12. The shaft sealing system of claim 11, wherein the substantially
rigid cylindrical body is formed of a non-ferrous metal
material.
13. The shaft sealing system of claim 11, wherein the outer groove
at the output end has a width that is narrower than a length of the
outer cylindrical surface at the power end of the annular seal
cavity.
14. The shaft sealing system of claim 11, wherein the substantially
rigid cylindrical body is split into two semi-circular halves along
a center-line.
15. The shaft sealing system of claim 14, wherein corresponding
alignment holes are formed in each semi-circular half of the
substantially rigid cylinder body and alignment pins are positioned
in the alignment holes.
16. The shaft sealing system of claim 11, wherein the outer surface
of the substantially rigid cylindrical body includes an O-ring
groove with an O-ring disposed therein.
17. The shaft sealing system of claim 11, further including at
least one compressible packing ring disposed adjacent the
substantially rigid cylindrical body on the power end of the
annular seal cavity.
18. The shaft sealing system of claim 11, wherein the substantially
rigid cylindrical body is dimensioned to provide a bearing surface
for the shaft.
19. A shaft sealing system for use in an annular seal cavity of a
mechanical device having an output end and a power end with a shaft
running through the seal cavity, comprising: a substantially rigid
cylindrical bearing formed with a sidewall dimensioned to fit into
the seal cavity; the sidewall of the bearing having an outer
cylindrical surface closely dimensioned to fit into the seal cavity
and having an inner bore closely dimensioned to fit over the shaft
to provide a bearing surface for the shaft; the outer cylindrical
surface formed with an outer groove with at least one flush hole
and the inner bore formed with an inner groove with at least one
flush hole, the inner groove at a location spaced apart from and
not aligned with the outer groove along the longitudinal axis of
the bearing to form a displaced integral lantern ring; the at least
one flush hole in the outer groove extending substantially radially
into the sidewall to a predetermined depth and the at least one
flush hole in the inner groove extending substantially radially
into the sidewall a predetermined depth; and at least one
substantially axial passage in the sidewall at the predetermined
depths connecting the at least one flush hole in the outer groove
to the at least one flush hole in the inner groove to form a
non-linear path between the inner and outer grooves within the
sidewall for passage of seal fluid through the displaced integral
lantern ring and to the shaft.
Description
BACKGROUND OF THE INVENTION
This invention relates to an improved bearing with an integral
lantern ring for a rotary mechanical device and, more particularly,
to an improved bearing with the lantern ring having offset outer
and inner flush holes.
Rotary mechanical devices, such as mixers and centrifugal pumps,
include an impeller mounted on a shaft which is driven by an
electrical motor. The shaft passes through a seal cavity or a
stuffing box defined by a cylindrical cavity in the device housing.
The shaft is supported by bearings at the motor end, and seals are
placed in the stuffing box to engage the shaft to prevent fluid
from passing through the seal cavity and reaching the bearing and
the motor, causing damage to both.
In mechanical pumps, chemical fluids or solvents being pumped, many
of which are corrosive, enter the seal cavity. Accordingly, it is
important that appropriate packing material is placed within the
seal cavity. In addition, fluid such as seal water is pumped into
the seal cavity through a flush port to prevent the fluid being
pumped or mixed from travelling along the shaft to the bearings and
motor and to provide lubricant to the packing. Over extended use,
the pump shaft may develop a whip as the bearings wear. Thus, it is
highly desirable to provide a sealing system that provides an
effective seal and an additional bearing surface to reduce the whip
that can occur as the shaft rotates, thus controlling the amount of
seal fluid entering an outer lantern ring groove in the seal
cavity.
While there are a wide variety of devices available for use in
providing sealing in a seal cavity, it is desirable to provide a
improved bearing and sealing system providing an additional bearing
surface for the impeller end of the shaft and causing a reduction
in the pumped or mixed fluid entering the seal cavity to be
countered by the seal fluid and packing to provide advantages over
available devices.
SUMMARY AND OBJECTS OF THE INVENTION
Generally speaking, in accordance with the invention, an improved
bearing with an integral diverted lantern ring for a rotary
mechanical device is provided. The bearing is a substantially rigid
member with an outer lantern ring groove at one location along the
bearing axis and an inner lantern ring groove at another location
along the bearing axis, with channels in the bearing wall to direct
seal fluid onto the shaft from the inner lantern ring groove. The
inner bore of the bearing provides a bearing surface for
eliminating whip in the device shaft. The bearing is split to
provide easy installation over an installed device shaft.
The bearing prepared in accordance with the invention is
substantially rigid and is typically manufactured of a non-ferrous
metal or thermoplastic material for providing an improved bearing
surface and resistance to industrial solutions. The inner bore of
the bearing closely approximates the outer diameter of the pump
shaft. The external surface of the bearing includes a groove for
receiving seal fluid with channels to an inner groove to form an
internal lantern ring. Typically, the outer lantern ring groove is
located at a flush inlet port near the impeller end of the stuffing
box, and the diverted flow exits the lantern ring at the inner
groove closer to the motor end. Generally, two or more packing
rings are added on the motor side of the bearing to complete the
installation.
Accordingly, it is an object of the invention to provide an
improved bearing with an integral lantern ring to be inserted into
a seal cavity of a rotary mechanical device.
Another object of the invention is to provide an improved bearing
with an integral lantern ring with an outer grove at one location
along the length of the bearing and an inner or internal groove
connected thereto at another location along the length of the
bearing.
Still another object of the invention is to provide an improved
bearing for a rotary mechanical device having an integral lantern
ring and a bearing outer O-ring for improved isolation of the
product being handled by the rotary device.
Yet another object of the invention is an improved bearing with an
integral diverted lantern ring for use with complementary flexible
packing rings for use in a shaft sealing system to be inserted into
the seal cavity of rotary mechanical devices.
A further object of the invention is to provide a bearing with an
integral lantern ring with an outer lantern ring groove and holes
closer to the impeller end of the seal cavity and an inner lantern
ring groove and holes closer to the motor end of the seal
cavity.
Still other objects and advantages of the invention will in part be
obvious and will in part be apparent from the specification and
claims.
The invention comprises a product possessing the features,
properties, and the relation of components which will be
exemplified in the product hereinafter described and the scope of
the invention will be indicated in the claims.
BRIEF DESCRIPTION OF THE DRAWINGS
For a fuller understanding of the invention, reference is made to
the following description taken in connection with the accompanying
drawings, in which:
FIG. 1 is a partial cross-sectional view of a typical rotary fluid
pump with a bearing in accordance with the invention installed in
the seal cavity;
FIG. 2 is an enlarged cross-sectional view of the seal cavity of
the pump showing a bearing with diverted lantern ring sealing
system in accordance with the invention in place in the seal
cavity;
FIG. 3 is a side elevational view of the bearing with diverted
lantern ring of FIG. 2 prepared in accordance with the
invention;
FIG. 4 is a perspective view of the bearing of FIG. 3;
FIG. 5 is a cross-sectional view along the line 5-5 in FIG. 3;
FIG. 6 is a cross-sectional view along the line 6-6 in FIG. 3;
and
FIG. 7 is a side elevational view of an embodiment of the invention
wherein the bearing of FIG. 2 includes an outer O-ring;
FIG. 8 is a perspective view of the two sections of the bearing of
FIG. 3.
DESCRIPTION OF THE PREFERRED EMBODIMENTS
FIG. 1 illustrates a generic form of a centrifugal pump 11 in
cross-section mounted on a frame 10. Pump 11 includes a centrifugal
impeller 12 driven by an electric motor 13 that drives a rotary
shaft 14 coupled to impeller 12. Shaft 14 is supported by a bearing
housing 16 and rotates to draw fluid in through an impeller inlet
17 and expel the fluid out through a radial impeller outlet 18.
Pump 11 includes a housing 19 having an inner bore 21 that defines
a seal cavity or stuffing box 22 with shaft 14 passing therethrough
as shown in detail in FIG. 2. Housing 19 includes an impeller
opening 23 through which shaft 14 passes to engage impeller 12 and
also includes a flush port 25 at the impeller end of stuffing box
22 for introduction of a flush fluid into stuffing box 22. Shaft 14
is coupled to impeller 12 by a nut or fastener 24 at the end
portion of shaft 14 projecting through impeller 12.
Pump 11 operates by drawing a fluid to be pumped into inlet 17.
During pumping, fluid tends to migrate and be forced into seal
cavity 22 through opening 23. A wide variety of seals and venting
configurations are available to be placed in seal cavity 22
abutting opening 23 in order to restrict and limit entry of pumped
fluid into seal cavity 22. If fluid enters seal cavity 22 and
migrates to bearings 32a, 32b, bearings 32a, 32b will be subject to
substantial degradation due to the corrosive action of the pumped
fluid.
FIG. 2 is an enlarged view of seal cavity 22 with a bearing with
diverted lantern ring 31 in accordance with the invention in place.
The motor end of seal cavity 22 is defined by a gland follower 27
mounted on gland bolts 28 and secured in place by gland nuts
29.
As shown in FIG. 2, bearing 31 constructed and arranged in
accordance with the invention is positioned against the impeller
end of seal cavity 22. A pair of compressible sealing rings 32a,
32b are positioned on the motor side of bearing 31. These elements
are secured within seal cavity 22 by gland follower 27. Examples of
various types of packing rings suitable for use herein are shown in
U.S. Pat. No. 5,370,926, U.S. Pat. No. 4,559,862, U.S. Pat. No.
4,431,698, U.S. Pat. No. 4,371,180, and U.S. Pat. No. 4,298,207,
the contents of which are incorporated herein by reference.
In FIG. 3, bearing 31 is shown in a side elevational view. Bearing
31 is custom made for a particular shaft and pump. Bearing 31 is
shown in perspective in FIG. 4.
Bearing 31 is a substantially cylindrical rigid member with an
outer surface 33 and with an inner bore 34 closely dimensioned to
the outer dimension of pump shaft 14 and fits within inner bore 21
of pump housing 19. Outer surface 33 of bearing 31 is formed with
an outer flush fluid groove 36 at the impeller end at the location
of flush port 25. Inner bore 34 of bearing 31 provides a bearing
surface for shaft 14 when in position as shown in FIG. 2, and this
is custom dimensioned for a particular mechanical device.
Bearing 31 is also formed with an inner flush fluid groove 37
formed in a location closer to the motor end to create a diverted
lantern ring. Inner seal fluid groove 37 is formed in a position
not adjacent to, that is, not aligned with, the location of outer
flush fluid groove 36. A plurality of flush fluid holes 38 formed
in outer bearing flush fluid groove 36 are in fluid communication
with flush fluid holes 45 in inner groove 37 through channels
46.
In the embodiment illustrated in FIGS. 1-3, outer lantern ring
groove 36 is closer to the motor end of stuffing box 22. The
purpose of providing the diverted lantern ring with holes 45 closer
to the motor end is to redirect the external flush from outer
groove 36 to inner groove 37 at the motor end. This increases the
throttling characteristic of the close clearance of the bearing
surface to the shaft.
In order to place bearing 31 in position in seal cavity 22, bearing
31 is split along a centerline 39, as shown in FIGS. 5 and 6.
Splitting bearing 31 along a diameter allows bearing 31 to be
placed about installed shaft 14 and pushed into position at the
impeller end of seal cavity 22. Generally, at least one or two
packing rings 32a, 32b are positioned on the gland side of bearing
31.
Bearing 31 split along center line 39 includes a pair of
corresponding holes 41 on both halves of split bearing 31 for
receiving mounting pins 42 for realignment and reassembly thereof.
In this construction, pins 42 insure that when bearing 31 is
secured about shaft 14, outer flush fluid groove 36 and inner
groove 37 are properly aligned on both sections. Outer flush fluid
groove 36 is positioned to align with flush port 25 formed in
housing 19.
FIG. 7 illustrates an embodiment of the invention wherein a bearing
with diverted lantern ring 51 includes an outer surface 52 with an
O-ring 53 groove positioned in seal cavity 22. An O-ring 54 is
positioned in O-ring groove 53 formed on outer surface 52 of
bearing 51. O-ring 54 can be formed of a variety of resilient
materials, including perfluoroelastomers or other resilient
material compatible with the pumped fluid for providing an
additional barrier to isolate the motor end of shaft 14 from fluid
entering seal cavity 22. An O-ring 54 provides an additional
obstacle to prevent fluid from entering seal cavity 22.
Bearing 31 or 51 is custom made for a particular shaft and pump.
Cross-sectional elevational views of the mating faces of bearing 31
before reassembly are shown in FIGS. 6 and 7. FIG. 8 is a
perspective of the two sections of an axially split bearing showing
four extraction holes 48 at the motor end of the A section of
bearing 31.
Many types of rotary equipment have the flush port close to the
impeller end of the stuffing box. Almost all of these operate with
heavy solids, such as mining and foods. Many pumps, such as Weir
Slurry Group (Warman Pumps) pumps, GIW (Georgia Iron Works) pumps,
Morris Pumps, and Krebs Pumps, and mixers (vertical and horizontal)
often times have the port located there. The theory is that in
order to keep slurry out of the stuffing box, the best position is
at the throat. The shortcoming with this view is that flush
pressure and volume are not equalized all the way around the
lantern ring before it goes into the process solids. By providing a
bearing with a close clearance bearing surface ahead of the exit
ports of the lantern ring, the close clearance between shaft and
bearing where the flush enters, forces equalization all the way
around, before the flush fluid gets to the throat.
The following Example is set forth by way of illustration to help
explain the invention, and is not intended to be limiting in any
way.
Example I
A bearing with an integral diverted lantern ring in accordance with
the invention is prepared as follows. The bearing is of a given
length with an A Section that is the extraction side with an inner
lantern ring groove and a B Section that is the impeller side and
is chamfered with an outer lantern ring groove.
1. A piece of tube stock of a selected material is cut to a length
corresponding to the total length of Sections A and B;
2. The piece is then cut into an A Section and a B Section;
3. End holes are drilled in the mating end faces of Sections A and
B;
4. Pins are inserted into the holes in the mating faces to
facilitate press-fit reassembly of the Sections A and B;
5. The combined Sections A and B are split in half axially.
6. The individual sections are milled, drilled and pinned and
reassembled for final machining;
7. O.D and I.D. are finish turned to a specific diameter;
8. An inner groove is formed in Section A, and outer groove is
formed in Section B, at predetermined locations;
9. Aligned flush holes are drilled in the O.D and I.D groove in
each Section A and B to a predetermined depth;
10. Flush channels are completed by drilling into mating faces of
each section to break through and connect to existing drill holes;
and
11. Extraction holes are drilled into the motor end of Section
A.
In this case bearing 31 of FIG. 3 has outer diameter 33 of 9.172''
and inner diameter 34 of 7.140'' and is 2.963'' in length. The A
section with inner groove 37 and extraction holes are cut to
1.482'' in length. Inner groove 37 is cut 0.250'' from the
extraction end and 0.625'' wide. The B section outer groove 36 cut
0.375'' from the impeller end to match flush port 25 port the
device. Flush holes 44 and 45 are 3/8'' in diameter and flush
channels 46 are completed by drilling into the mating faces of each
section.
The dimensions set forth above are representative and not limiting
of the invention. The actual dimensions of aspects of bearings to
be prepared and installed according to the invention will vary
according to the particular application.
Bearings 31 and 51 are substantially rigid and formed of materials
which will not be attacked or destroyed by corrosive fluids being
transported by pump 11. Preferred materials of construction include
non-ferrous materials, molybdenum/-carbon or glass filled
thermoplastic material, such as polytetrafluoroethylene (PTFE) or
other suitable plastic material. Materials are selected that can
provide a suitable bearing surface and are resistant to most
industrial solutions. Suitable bearing materials are those that
provide suitable chemical, temperature, compressive strength,
flexural strength and wear characteristics and can be appropriately
machined to yield the desired bearing dimensions and tolerances.
Such bearing materials include, but are not limited to, polymers,
including polyphenylene sulfides, polyimidizoles, polyamideimides,
polybenzylimidizoles, PEEK polymers obtained by step-growth
polymerization by the dialkylation of bisphenolate salts, PTFE,
perfluoroalkoxy, and formulations containing these polymers in a
major proportion.
Packing materials are described in the aforementioned U.S. Pat. No.
4,298,207, No. 4,371,180, No. 4,431,698, No. 4,559,862, and No.
5,370,926, the contents of each of which are incorporated herein by
reference in their entirety. More particularly, useful materials
include, but are not limited to, mechanically and/or thermally
resilient component of graphite tape, expanded graphite foil,
graphite fiber, carbon fiber, polybenzimidazole (PBI) fiber, PEK
fiber, PEEK fiber, PFA fiber, aromatic polyamide fiber, Inconel or
Monel wire, or combinations thereof. In another aspect of the
invention, the at least one packing member is a material selected
from the group consisting of carbonized yarns, graphitized yarns,
exfoliated graphite yarns, ceramic yarns, and glass yarns. Tension
or lip seal rings may comprise the same or different components of
the same or different components. The packing rings or members may
comprise mechanically and/or thermally components, whether
individually or by combinations thereof, i.e., corner yarns,
resilient core, etc. The designs and materials are chosen to resist
packing consolidation.
Braided packing rings may include fibers of flax, jute, asbestos,
or a synthetic material, such as polytetrafluoroethylene, which
fibers are formed into yarns or strands and which are braided
together about core strands. The result is typically a packing
having a square cross-section and herringbone weave pattern
extending in an axial direction along the packing Typical packing
members are illustrated in U.S. Pat. No. 3,646,846, incorporated
herein by reference.
In order to place bearing 31 in position in seal cavity 22, bearing
31 is preferably split along a centerline 39. Splitting bearing 31
along a diameter allows bearing 31 to be placed about installed
shaft 14 and pushed into position at the impeller end of seal
cavity 22. Generally, at least one or two packing rings 32a, 32b
are positioned on the gland side of bearing 31.
Bearing 31 split along center line 39 includes a pair of
corresponding holes 42 on both halves of split bearing 31 for
receiving mounting pins 42 for realignment and reassembly of
bearing 31. In this construction, pins 42 insure that when bearing
31 is secured about shaft 14, outer seal water groove 36 and inner
groove 37 are properly aligned on both sections. Outer seal water
groove 36 is dimensioned and positioned to align with a flush port
25 formed in housing 19.
It can readily be seen that the bearing with integral diverted
lantern rings as part of a cylindrical seal and seal system
constructed in accordance with the invention can be easily
installed in a conventional rotary impeller pump with pins to
guarantee alignment of the seal upon installation. This
configuration allows seal fluid to contact the shaft closer to the
motor end. Generally, two packing rings or more are added to
complete installation of an effective sealing system. When in
place, the bearing will support the impeller end of the pump shaft,
providing an additional bearing surface to aid in eliminating the
whip commonly found in pump and other rotary equipment shafts.
Since the clearance between the pump shaft and the bearing is
relatively small, flush fluid entering the lantern ring groove
would be considerably throttled, thereby minimizing the quantity of
seal water flushing and lubricating the bearing and finally
entering into and diluting the product being pumped.
It will thus be seen that the object set forth above, among those
made apparent from the preceding description are efficiently
attained and, since certain changes may be made in the device set
forth without departing from the spirit and scope of the invention,
it is intended that all matter contained in the above description
and shown in the accompanying drawings shall be interpreted as
illustrative and not in a limiting sense.
It is also to be understood that the following claims are intended
to cover all of the generic and specific features of the invention
herein described and all statements of the scope of the invention,
which, as a matter of language, may be said to fall there
between.
* * * * *